WO1995023293A1 - Direct drive valve - Google Patents
Direct drive valve Download PDFInfo
- Publication number
- WO1995023293A1 WO1995023293A1 PCT/FR1995/000216 FR9500216W WO9523293A1 WO 1995023293 A1 WO1995023293 A1 WO 1995023293A1 FR 9500216 W FR9500216 W FR 9500216W WO 9523293 A1 WO9523293 A1 WO 9523293A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- drawer
- axis
- motor
- arm
- exhaust
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86622—Motor-operated
Definitions
- the invention relates to a mechanical control energy transmission device, in particular for applications in the automotive field such as controlling the braking pressure in a brake or the rapid correction of a hydropneumatic suspension.
- hydraulic systems such as hydraulic servo-valves seem to be the best suited to be embedded in vehicles or other mobile equipment because they are inexpensive and can be easily adapted and quickly to the requirements of new technical or economic conditions.
- a hydraulic servo valve can be defined as the interface between an electrical or electronic device providing a control signal, and a hydraulic device that must provide a response depending on the electrical signal.
- pressure control in a brake control for example,
- the servo valve must have a high bandwidth so as to allow a quick and stable response from servo, regardless of the hydraulic flow requested.
- the servo valve must be compatible with the automotive environment by:
- a servo valve meeting all these characteristics consisting of a rotary actuator such as a rotary electric motor of low inertia, controlled in position and connected by mechanical connection means to a mechanical member such as a hydraulic distributor with drawer linear, the motor being equipped with a return spring in its initial position.
- Such a device is well suited to be carried on a vehicle because the rotary electric motor is insensitive to vibrations and accelerations which have no effect on its angular position, which is not the case for a linear motor whose metallic mass can be displaced by inertia effect.
- the hydraulic distributor with linear drawer it is already widely used in the automotive industry because it is inexpensive, not very sensitive to impurities and the very low mass of the drawer itself means that accelerations along its axis only create very low forces.
- the invention aims to remedy these drawbacks by proposing a mechanical control energy transmission device, comprising an actuator or rotary motor and connecting means connecting this actuator to a mechanical member such as a hydraulic slide to transmit a linear movement to the latter, characterized in that it comprises means for taking up play and returning the mechanical member to a predetermined safety position.
- the drawer being able to establish or prevent communications between at least one use and either a high pressure source or an exhaust
- the predetermined safety position is a position in which communication is established between said use on the one hand and the high pressure source or exhaust on the other hand;
- the play take-up and return means of the mechanical member act directly on the drawer;
- the play take-up and return means of the mechanical member comprise a spring or the like acting on one end of the drawer;
- the axis of rotation of the motor is perpendicular to the axis of the drawer;
- the connecting means comprise a lever secured to the rotor of the motor and an arm of which, located at a certain distance from the axis of rotation of the latter, acts on a part secured to the drawer;
- the lever comprises a first arm extending perpendicular to the axis of rotation of the motor and one end of which is fixed to the rotor at this axis, and a second arm, constituting the aforementioned arm, extending perpendicular to the first;
- - Said arm is connected to the drawer by a connecting rod whose two ends are articulated respectively on the arm and the drawer by means of ball joints;
- the engine is approximately in the middle of its stroke, .
- the lever is perpendicular to the axis of the drawer,
- the axis of the drawer coincides with the axis of the arm or of the ball joint of the lever;
- the connecting means comprise at least one roller integral with the drawer and with an axis perpendicular thereto, sliding in a helical ramp formed in the wall of a cylindrical part driven by the motor in rotation about its own axis, which is parallel, and preferably collinear, to that of the motor, and means for holding the axis of said roller in translation in a direction parallel to the axis of the slide;
- Said means for holding in translation comprise at least one guide roller of the same axis as the first and also integral with the drawer, this guide roller being able to roll in a groove parallel to the axis of the drawer formed in a fixed part;
- connection means include:
- a first plate arranged perpendicular to the axis of the engine and driven in rotation by the latter;
- a first branch the ends of which are articulated on each of the two plates; and a second branch making a non-zero angle with the first and acting on one end of the drawer;
- the drawer comprising a rod provided with blocks sliding in a bore formed in a jacket and capable of releasing or sealing radial holes communicating with said use, the high pressure source and the exhaust, the holes have a circular section;
- the drawer comprising a rod provided with sliding blocks in a bore formed in a jacket and capable of releasing or closing radial holes communicating with said use, the high pressure source and the exhaust, at least one of the holes has a non-circular section and adapted so that it increases progressively and regularly as it is released by the corresponding block when the drawer is moved;
- - Said hole has a circular section or the like on one side and ends in a point on the opposite side.
- the hole (s) opens (s) into an annular groove formed outside the jacket of the drawer and / or into an annular groove formed on the wall of the bore;
- the bore has two holes each communicating with a use, two holes communicating with
- FIG. 1 is a schematic perspective view of a device according to the invention, the motor axis being perpendicular to that of the drawer;
- FIG. 2 is a section along the line II-II of Figure 1;
- FIG. 3 is a sectional view along line III-III of Figure 2;
- FIGS. 4a to 4d are schematic sectional views on an enlarged scale illustrating several possible embodiments of the hydraulic slide
- FIG. 5 is a schematic perspective view of the connection between the motor and the drawer using ball joints
- Figure 6 is a view similar to Figure 5 with partial cutaway showing the ball joints
- FIG. 7 is a schematic sectional and perspective view of an embodiment in which the axis of the motor is collinear to that of the drawer;
- FIG. 8 is a sectional view in elevation of the device of Figure 7;
- FIG. 9 is a schematic sectional view in perspective of another embodiment, still with the axis of the motor collinear with that of the drawer;
- FIG. 10 is a sectional view in elevation of the device of Figure 9;
- FIG. 11a to 11d are schematic sectional views on an enlarged scale of various forms of the dispenser having or not annular grooves and with different sections of holes; and
- FIG. 12 is a graph giving the flow rate as a function of the stroke of the slide for various embodiments illustrated in Figures 11a to 11d.
- FIG. 1 illustrates a first embodiment of the device which is the subject of the invention comprising a rotary electric motor 1 mounted in a casing 2, part of which is cut away in the drawing.
- the rotation of the motor drives a lever 3, which will be described in more detail later, which ends in an arm 4, the end of which 4a is received in a yoke-shaped part 5 provided at one end of the drawer 6 of the distributor 7.
- Reference 8 designates the housing thereof in which are drilled holes 9 for communication with various elements of the hydraulic circuit such as high pressure source, exhaust, various uses.
- the axis of the arm 4 is parallel to the axis of rotation of the motor, these two axes being perpendicular to that of the slide.
- FIG. 2 shows more precisely the shape of the yoke 5 and of the drawer 6, which essentially consists of a rod 10 provided with two blocks PI and P2 sliding in a bore 11 of a jacket 12, it - even mounted in the housing 8.
- a return spring R interposed between a part such as a plug 13 secured to the housing 8 and the end of the drawer opposite the yoke 5, ensures, in accordance with the main characteristic of the object device of the invention, the take-up of the games of the connection and the return of the drawer to a predetermined position in the event of the connection being broken.
- the arm 4 is linked to the motor rotor by the lever 3 so that a low amplitude oscillation of the rotor around the axis A causes movement of the arm 4 in an arc of circle centered on A and tangent to the axis of the drawer: this has the effect of moving the drawer linearly along its axis because it is guided in translation by the bore 11.
- the end 4a of the arm 4 in contact with the yoke is in the shape of a barrel, the axis of the barrel being coincident with that of the arm 4, as can be seen in FIG. 3: this allows a little freedom so compensate for possible misalignments, while minimizing contact pressures between the two parts.
- FIGS. 4a to 4d illustrate various possible embodiments for the drawer 6.
- FIG. 4a which is the simplest, corresponds to FIG. 2 and we find the rod 10 provided with the blocks PI and P2 sliding in the bore 11 of the jacket 12.
- the latter is pierced with three orifices 9 ensuring communication respectively with a high pressure source, an exhaust and a use; these three communications are symbolized by the letters H, E and U respectively and the latter opens into the bore 11 halfway between H and E.
- the holes drilled in the jacket are in alignment with those drilled in the housing and c ' is why they carry the same reference.
- Figures 4c and 4d correspond to an embodiment in which there are two uses Ul and U2.
- the high pressure H opens out in the middle between Ul and U2 while the exhaust E communicates with the bore 11 through two orifices located beyond Ul and U2.
- FIGS. 4c and 4d shows that, if Ul is at the exhaust, U2 communicates with the high pressure and vice versa.
- FIG. 5 The perspective view of FIG. 5, deliberately very simplified, only shows the front face of the motor 1, the slide 6 and their connection.
- the lever 3 which consists of a first arm 13, extending perpendicular to the axis of the motor and one end of which is fixed to the latter, and of a second arm 4 fixed to the other end of the first and extending perpendicular to this first arm 13.
- a connecting rod 14 provides the connection between the lever 3 and the drawer 6 by means of ball joints visible in the view with the cutaway in FIG. 6.
- the end 4a of the arm 4 and the end 6a of the drawer are constituted by form of ball joints received in corresponding housings of the aforementioned connecting rod 14.
- the assembly is carried out so that in the central position of the drawer , that is to say with an equal overlap for the intake and 1 • exhaust:
- the lever 3 is perpendicular to the axis of the drawer; - the axis of the drawer is concurrent with the axis of the arm 4 or of the ball joint 4a of the lever.
- the lever 3 is perpendicular to the axis of the drawer
- the arm 13 of this lever or the plane containing the two arms 13 and 4) which is perpendicular to the axis of the drawer.
- the axis of the ball it is the axis of its tail which, in the case of Figure 6, is constituted by the arm 4 itself.
- the relationship between the angle of rotation of the motor and the stroke of the slide is determined by the configuration and dimensions of the lever.
- Figures 7 and 8 on the one hand, 9 and 10 on the other hand, illustrate two constructions in which the axis of the motor is collinear with that of the drawer.
- connection is essentially constituted by a cylindrical part 15 with an axis coincident with that of the motor and driven directly by the latter.
- the part 15 has a helical groove 16 in which a roller 17 can move, mounted at one end of a shaft 18 provided at one end of the drawer 6 and extending perpendicularly to the latter, the axis of rotation of the roller being confused with that of tree 18.
- Two guide rollers 19 are mounted on the shaft 18 on either side of the drawer 6 with the same orientation as the roller 17 and can slide in grooves 20 parallel to the axis of the drawer formed in a part 21 integral with the housing 8 of the latter: thus, the rollers 17 and 19 and the shaft 18 can only move in translation along the axis of the drawer.
- cylindrical part 15 is closed at its end situated on the motor side and open at its other end in order to receive the corresponding end of the drawer and the part 21.
- the rotation of the motor 1 causes that of the cylindrical part 15 and the groove 16 drives the roller 17, which has the effect of linearly displacing the drawer since the rollers can only move in translation along the axis thereof .
- FIGS. 7 and 8 clearly show the orifices 9 making the distributor 7 communicate with the rest of the hydraulic circuit as well as the spring R ensuring the take-up of play and the return of the drawer in the event of the links being broken.
- the drawer 6 is preferably connected to the shaft 18 by a ball joint 6a to compensate for possible misalignments.
- the motor is arranged as above, but the connection consists of two circular plates 22 and 23 arranged opposite and whose axis coincides with 1 " axis A common to the motor and to the drawer.
- the first 22 of the plates is rotated by the motor while the other 23 is fixed to the housing 8 of the distributor 7.
- levers 24 consisting of an arm 25 extending between the plates, one end of which is articulated on each of the plates 22,23 by ball joints 26,27 respectively and the other end of which is articulated on a ball joint 28 integral with the drawer.
- the common axis of the ball joints 26 and 27 is perpendicular to the arm 25 and they somehow constitute therewith two branches perpendicular to each other.
- the arm 25 In the neutral position, the arm 25 extends parallel to the plates and the axis of the ball joints 26 and 27 is parallel to that of the drawer.
- the rotation of the motor causes that of the plate 22: as the plate 23 is fixed, the axis of the ball joints 26 and 27 ceases to be parallel to the drawer and the arm 25 changes orientation, causing the displacement of the drawer 6 by the intermediate of the ball 28.
- the constitution of the dispenser is the same as in FIGS. 7 and 8 with the orifices 9, the return spring R and the ball joint 6a by which the drawer 6 is articulated on the part carrying the ball joints 28. If necessary, provision can be made an additional return spring RI interposed between the motor 1 and the plate 22.
- FIGS 11a to 11d illustrate several possible embodiments of the dispenser used in the device which is the subject of the invention. In all cases, there are only two blocks PI and P2 and three communications with a high pressure source, an exhaust and a single use.
- FIG. 11a corresponds to the simplest case (similar to FIG. 4a) in which the holes in the jacket 12 and the housing 8, which constitute each orifice 9, are of circular section, of the same diameter, and continuously one with the other.
- FIG. 12 gives, for different configurations of the distributor, the shape of the flow laws (in liters per minute) as a function of the stroke of the slide (in millimeters) as and when the corresponding block clears the orifice considered, for feeding at a pressure of 100 bars.
- curves C1 to C3 correspond to the figure lie for different angles at the top of the part 30, h being the height of the aforesaid isosceles triangle.
- Curve C4 corresponds to a circular hole with a diameter of 3 mm according to FIG. 11a and curve C5 to the presence of an internal groove in accordance with FIG. 11d.
- the device which is the subject of the invention therefore has particularly advantageous advantages since on the one hand the rotary motor is insensitive to parasitic accelerations and vibrations and, on the other hand, the absence of play in the mechanical connections obtained thanks to the return means. results in greater precision in the positioning of the drawer and prevents premature wear of the parts. In addition, in the event of a break in the mechanical connections, the drawer assumes a perfectly determined position. Finally, if the above description has been made in the context of an automotive application, the device which is the subject of the invention can be used in any type of installation, whether it be mobile equipment or stationary machinery .
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Mechanically-Actuated Valves (AREA)
- Electrically Driven Valve-Operating Means (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95910591A EP0695398A1 (en) | 1994-02-24 | 1995-02-23 | Direct drive valve |
JP52217695A JPH08509538A (en) | 1994-02-24 | 1995-02-23 | Direct drive valve |
US08/978,880 US6334462B1 (en) | 1994-02-24 | 1995-02-23 | Mechanically-controlled power transmission device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9402127A FR2716514B1 (en) | 1994-02-24 | 1994-02-24 | Mechanical control energy transmission device. |
FR94/02127 | 1994-02-24 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/978,880 Continuation US6334462B1 (en) | 1994-02-24 | 1995-02-23 | Mechanically-controlled power transmission device |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1995023293A1 true WO1995023293A1 (en) | 1995-08-31 |
Family
ID=9460395
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR1995/000216 WO1995023293A1 (en) | 1994-02-24 | 1995-02-23 | Direct drive valve |
Country Status (5)
Country | Link |
---|---|
US (1) | US6334462B1 (en) |
EP (1) | EP0695398A1 (en) |
JP (1) | JPH08509538A (en) |
FR (1) | FR2716514B1 (en) |
WO (1) | WO1995023293A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AUPQ515100A0 (en) * | 2000-01-19 | 2000-02-10 | Amcor Limited | Measurement apparatus and technique for properties of board product |
DE10135511C1 (en) * | 2001-07-20 | 2003-04-17 | Leica Microsystems | Device and method for adjusting components of an optical or mechanical system |
US7112156B2 (en) * | 2004-02-25 | 2006-09-26 | General Motors Corporation | Transmission with miniature motor for control to oil flow |
JP4559822B2 (en) * | 2004-11-02 | 2010-10-13 | ピー・エス・シー株式会社 | Gas pressure control valve |
FR2978998B1 (en) * | 2011-08-08 | 2013-07-26 | Sonceboz Automotive Sa | COMPACT DOSING DEVICE |
GB2587945B (en) * | 2018-05-17 | 2023-04-12 | Kawasaki Heavy Ind Ltd | Spool valve |
CN109094832A (en) * | 2018-07-09 | 2018-12-28 | 温州海德能环保设备科技有限公司 | A kind of water filtering antisludging agent automatic ration filling apparatus |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3818926A (en) * | 1973-04-11 | 1974-06-25 | D Wohlwend | Hydraulic valve and system |
EP0080888A2 (en) * | 1981-12-02 | 1983-06-08 | Pneumo Abex Corporation | Electro-mechanical direct drive valve servo system with rotary to linear valve drive mechanism |
EP0100480A1 (en) * | 1982-07-29 | 1984-02-15 | Pall Corporation | Duplex cam-operated pressure-balanced sleeve valve |
FR2538495A1 (en) * | 1982-12-24 | 1984-06-29 | Kugelfischer G Schaefer & Co | HYDRAULIC VALVE PROPORTIONAL, ELECTRICALLY ACTUATED |
EP0164469A1 (en) * | 1984-05-07 | 1985-12-18 | Pneumo Corporation | Direct drive valve and force motor assembly |
EP0192891A1 (en) * | 1985-01-28 | 1986-09-03 | Pneumo Abex Corporation | Spherical ball drive mechanism for a direct drive valve |
GB2201262A (en) * | 1987-02-16 | 1988-08-24 | Rexroth Mannesmann Gmbh | Servo-valve control |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1590581A (en) * | 1976-10-14 | 1981-06-03 | Hawker Siddeley Dynamics Eng | Electro-hydraulic systems |
US4133511A (en) * | 1977-01-26 | 1979-01-09 | Frieseke & Hoepfner Gmbh | Electro-hydraulic regulating valve system |
GB2085129B (en) * | 1980-10-09 | 1985-04-03 | Kontak Mfg Co Ltd | Valve actuator |
US4503888A (en) * | 1983-10-04 | 1985-03-12 | Mts Systems Corporation | Servovalve spool control for digital rotary servovalve |
US4645178A (en) * | 1985-11-22 | 1987-02-24 | Pneumo Abex Corporation | Redundant drive mechanisms for a direct drive valve and force motor assembly |
US4741365A (en) * | 1986-08-04 | 1988-05-03 | Mcdonnell Douglas Corporation | Compound pneumatic valve |
US5036886A (en) * | 1988-12-12 | 1991-08-06 | Olson Controls, Inc. | Digital servo valve system |
-
1994
- 1994-02-24 FR FR9402127A patent/FR2716514B1/en not_active Expired - Fee Related
-
1995
- 1995-02-23 WO PCT/FR1995/000216 patent/WO1995023293A1/en not_active Application Discontinuation
- 1995-02-23 EP EP95910591A patent/EP0695398A1/en not_active Withdrawn
- 1995-02-23 US US08/978,880 patent/US6334462B1/en not_active Expired - Fee Related
- 1995-02-23 JP JP52217695A patent/JPH08509538A/en active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3818926A (en) * | 1973-04-11 | 1974-06-25 | D Wohlwend | Hydraulic valve and system |
EP0080888A2 (en) * | 1981-12-02 | 1983-06-08 | Pneumo Abex Corporation | Electro-mechanical direct drive valve servo system with rotary to linear valve drive mechanism |
EP0100480A1 (en) * | 1982-07-29 | 1984-02-15 | Pall Corporation | Duplex cam-operated pressure-balanced sleeve valve |
FR2538495A1 (en) * | 1982-12-24 | 1984-06-29 | Kugelfischer G Schaefer & Co | HYDRAULIC VALVE PROPORTIONAL, ELECTRICALLY ACTUATED |
EP0164469A1 (en) * | 1984-05-07 | 1985-12-18 | Pneumo Corporation | Direct drive valve and force motor assembly |
EP0192891A1 (en) * | 1985-01-28 | 1986-09-03 | Pneumo Abex Corporation | Spherical ball drive mechanism for a direct drive valve |
GB2201262A (en) * | 1987-02-16 | 1988-08-24 | Rexroth Mannesmann Gmbh | Servo-valve control |
Also Published As
Publication number | Publication date |
---|---|
US6334462B1 (en) | 2002-01-01 |
FR2716514B1 (en) | 1996-04-05 |
JPH08509538A (en) | 1996-10-08 |
EP0695398A1 (en) | 1996-02-07 |
FR2716514A1 (en) | 1995-08-25 |
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